US5662018A - Working machine for material webs, particularly paper format cross-cutter - Google Patents

Working machine for material webs, particularly paper format cross-cutter Download PDF

Info

Publication number
US5662018A
US5662018A US08/442,947 US44294795A US5662018A US 5662018 A US5662018 A US 5662018A US 44294795 A US44294795 A US 44294795A US 5662018 A US5662018 A US 5662018A
Authority
US
United States
Prior art keywords
knife
gear
pressure medium
knives
working machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/442,947
Other languages
English (en)
Inventor
Hansjorg Klein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bielomatik Leuze GmbH and Co KG
Original Assignee
Bielomatik Leuze GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bielomatik Leuze GmbH and Co KG filed Critical Bielomatik Leuze GmbH and Co KG
Assigned to BIELOMATIK LEUZE GMBH & CO. reassignment BIELOMATIK LEUZE GMBH & CO. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KLEIN, HANSJORG
Application granted granted Critical
Publication of US5662018A publication Critical patent/US5662018A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/56—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which travels with the work otherwise than in the direction of the cut, i.e. flying cutter
    • B26D1/62—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which travels with the work otherwise than in the direction of the cut, i.e. flying cutter and is rotating about an axis parallel to the line of cut, e.g. mounted on a rotary cylinder
    • B26D1/626—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which travels with the work otherwise than in the direction of the cut, i.e. flying cutter and is rotating about an axis parallel to the line of cut, e.g. mounted on a rotary cylinder for thin material, e.g. for sheets, strips or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D5/08—Means for actuating the cutting member to effect the cut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/56—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which travels with the work otherwise than in the direction of the cut, i.e. flying cutter
    • B26D1/62—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which travels with the work otherwise than in the direction of the cut, i.e. flying cutter and is rotating about an axis parallel to the line of cut, e.g. mounted on a rotary cylinder
    • B26D2001/623—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which travels with the work otherwise than in the direction of the cut, i.e. flying cutter and is rotating about an axis parallel to the line of cut, e.g. mounted on a rotary cylinder for selecting different knife sets by shifting the angle of the rotary cylinder
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19623—Backlash take-up
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/465—Cutting motion of tool has component in direction of moving work
    • Y10T83/4766—Orbital motion of cutting blade
    • Y10T83/4795—Rotary tool
    • Y10T83/483—With cooperating rotary cutter or backup
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/929—Tool or tool with support
    • Y10T83/9372—Rotatable type
    • Y10T83/9396—Shear type
    • Y10T83/9399—Cutting edge wholly parallel to axis of rotation

Definitions

  • the invention relates to a working machine for material webs, particularly a paper format cross-cutter, with two machine parts rotatable in opposition and in particular knife shafts with knives on the circumference forming at least one knife set, the rotary machine parts being synchronized with one another by at least one gear pair having at least one gear body and a tooth system.
  • size or format cross-cutters is normally used for cross-cutters, which cut from material webs divided up into strips by different formats, e.g. the standard DIN A 3 of DIN A 4 formats.
  • Normally two or three knives are located on each knife shaft and the knife shafts are so associated with one another that a cutting engagement is in each case produced between two knives set in matching manner.
  • cutting engagement is used to mean as association of the two knives which is such that there is a perfect cut between them.
  • the knives need not and should not be in contact with one another.
  • the so-called synchronous length of cut between two cuts is determined by the circumferential distance between knives on the particular knife shaft, because it is necessary that during the cutting engagement the web speed and the peripheral speed of the knives coincide. Thus, only one format length can be cut during a uniform rotation of the knife shafts.
  • DE-A-3,608,111 discloses clamp collars by means of which the synchronization gears can be fixed to the knife shafts. These clamp collars have a rotating gap filled with a pressure medium. As a result of the rotating gap a certain radial elasticity existed making it possible to set the somewhat eccentrically manufactured gear at one point of the circumference to a minimum backlash. The radial elasticity prevented a seizing of the gears.
  • Backlash is defined by Webster's Universal Unabridged Dictionary, 1936 Edition, as the backward surge of a pair or a train of toothed wheels acting under a variable driving pressure; the loose play of such a part. Backlash equals the clearance allowance between the flanks of the teeth in gear.
  • U.S. Pat. No. 3,182,540 discloses a paper cross-cutter, which carries on a knife shaft numerous knives, which cooperate with a roller-like counterroll for performing a squeezing cut. On it surface the counterroll has raised and lowered areas, so that through a specific reciprocal configuration of knife shaft and counterroll only certain knives perform the squeezing cut in each case, so that a different format length can be set.
  • German Patent 602,721 it is also known from German Patent 602,721 to engage for cutting purposes only two knife shafts equipped in each case with knives by means of a hand lever. As a result of a cam control they are forced apart again subsequently.
  • DE-A-4,005,028 describes two knife shafts equipped with knives, which use the opposing knife shaft as an anvil roller for performing a squeezing knife cut.
  • a corresponding knife configuration alternately longer and shorter portions (intermediate strips) can be cut out.
  • the object of the invention is to provide a working machine for material webs, which offers improved setting possibilities for two rotatable machine parts.
  • a cross-cutter improved compared with the prior art is to be provided, which has a better adaptability to the operating conditions and in particular permits an adaptation to different lengths of cut without or with only slight losses of cutting speed and without any significant conversion costs.
  • means are provided for minimizing the backlash in at least one circumferential sector of at least one gear.
  • gear is so radially widened preferably by hydraulic clamping means or e.g. mechanically by screw-in wedges or cones, at the points where the individual knife sets come into cutting engagement, that there is a so-called beat eccentricity, or high point, or point of greatest eccentricity, and the gear functions without backlash at this point.
  • the possibility of setting the backlash at different sectors makes it possible to provide several sector setting means over the circumference of a gear. This can be brought about by sector deformation, that is, deformation of a sector of the working circumference of the gear with respect to the rotational symmetry.
  • the tooth profiles can be displaced in the corresponding sector in the direction of the gear in engagement therewith, e.g. in the case of an externally toothed gear by a slight widening of the gear rim in this sector.
  • a particularly advantageous embodiment has a pressure medium pocket restricted to one circumferential portion of the gear and into which is pumped a liquid pressure medium, e.g. hydraulic fluid.
  • This pressure medium pocket e.g. a narrow slot extending circumferentially over a certain sector within the tooth system can also be closed to the outside by a weld and can be connected to a pressure medium feed line by means of a shutoff valve.
  • the size of the sector i.e. the length of the slot in the circumferential direction can be adapted to the requirements over the length of the backlash-free area. Even if it is only necessary to have a zero backlash in the vicinity of a single tooth, the pressure medium pocket will extend over several teeth in order to bridge the gap with the minimum divergence from the circular shape.
  • the profile of this web can also be used axially for influencing the bending line and therefore the outer contour of the gear in the micron range.
  • the sector setting possibility is particularly advantageous in the case of cross-cutters having several knives on both knife shafts and which are so set with respect to one another that different cutting engagements form in a specific rotation position association of the knife shafts to one another.
  • the gears synchronizing to two knife shafts can be set by means of the sector setting means to prevent backlash at the engagement positions.
  • Preferred setting means can have at least one, more particularly pressure medium-operated locking coupling provided with a radial tooth system.
  • This radial tooth system can be located between two collars, whereof one is connected in non-rotary manner to the particular knife shaft and the other to a synchronization gear of a knife shaft.
  • These radial tooth systems can be bridged by a corresponding radial tooth system on an axially movable connecting body. The latter forms a positive detent, which is only loaded in shear and can be made backlash-free by a corresponding tooth construction.
  • Such setting means can be provided for the connection of the knife shafts by two synchronization gear sets on each of the said gear sets.
  • the knives of the other knife set pass through the cutting gap without there being a corresponding counterknife there.
  • a passage e.g. a recess in the knife shaft surface
  • the material web which is not to be cut at this point, can optionally give way here.
  • the material web normally comprises several layers, which during the cutting the paper webs are brought together from several individual rolls to form a common layer passed through the overall machine. In the form of such layers they are longitudinally and transversely cut, superimposed in scale or flake manner, stacked and then removed in reams.
  • the standard formats of 11 and 17 inches in the USA are approximately in a ratio of 2:3 to one another.
  • DIN formats with 1.41 or 2.0 to the in each case larger size have ratios close to 2:3 or 1:2.
  • knife sets of in each case 1 and 2 or 2 and 4 knives can be bridged by per se known methods using a drive with varying velocity ratio, e.g. a direct motor drive according to DE-A-3,608,111, without any significant losses to the production speed.
  • knife sets with different characteristics, such as material (steel/hard metal), construction, setting and in particular cutting angle configuration and the like. In each case optimum conditions can be obtained for different operating conditions and material web types without requiring any knife shaft change. It is also possible to use two knife sets of the same type and same number of knives under the standpoint of extending the service life between knife changes.
  • two knife sets which are so displaced against one another on both knife shafts that in a specific rotation position association of the two knife shafts only one of the sets is in engagement, whereas the other knives pass through the cutting gap without cooperating with a corresponding counterknife.
  • FIG. 1 is a diagrammatic side view of two cooperating knife shafts in engagement position of a knife set.
  • FIG. 2 is a larger-scale detail of FIG. 1.
  • FIGS. 3 and 4 are representations corresponding to FIG. 2 in each case during an inactive knife passage through the cutting gap.
  • FIG. 5 shows the knife shafts according to FIG. 1 during adjustment for the engagement of a knife set.
  • FIG. 6 shows the knife shafts in cutting engagement of the second knife set.
  • FIG. 7 is a part section through the end portions of two knife shafts.
  • FIG. 8 is a detail of FIG. 4.
  • FIG. 9 is a detail of FIG. 7.
  • FIG. 10 is a section along line X in FIG. 9.
  • a cross 11 has two knife shafts 12,13, which are driven synchronously in opposition to one another in a manner described hereinafter relative to FIG. 7.
  • the knife shafts are in part over 2000 mm long, usually hollow drums of high strength materials, which in the case of a minimum weight are to have a maximum flexural and torsional stiffness.
  • clamping or fixing devices 28 are adjustably fixed five knives on each knife shaft belonging to two knife sets A and B (FIG. 1).
  • the knife set A contains three knives A1 to A3 arranged with a uniform spacing of 120° on the circumference of the knife shaft, whereas the two knives B1 and B2 of the knife set B are in each case 180° from one another on the circumference. To avoid an excessively hard cut the knives can be given a slight helical stagger.
  • the knives of the two knife sets A and B are so positioned with respect to one another that they do not drop below a certain circumferential distance. With the chosen arrangement 2/3, as shown in FIG. 1, there are 30° between knives A1 and B1 or A3 and B2.
  • the knives of the upper knife shaft 12 project somewhat over the knife shaft surface 14 and are introduced into small recesses 29, which are provided in the vicinity of the knife cutting edge 20 in the knife shaft surface 15 of the lower knife shaft 13.
  • the knives of the lower knife shaft 13 do not project over the knife shaft surface 15.
  • FIG. 1 shows the cutting engagement between the knives A1. It can be seen that the cutting gap 16, i.e. the area of the knife shafts located in the vicinity of the connecting line 17 between the axes 18 of the knife shafts 12,13 where they are closest together and in which the travel circles 19 of the knife cutting edges 20 overlap, is traversed by the material web 21.
  • the knives are slightly inclined with respect to the radial to the knife shaft, so that during insertion in the cutting position 22 shown in FIG. 1 they are aligned with one another in the longitudinal direction.
  • Cutting takes place on passing through this cutting gap 16.
  • the material web 21 passes through the cutting gap with the same speed as the peripheral speed of the travel circles 19 of the knife cutting edges 20.
  • a slight deflection of the material web at right angles to its running direction in this area is at its least prejudicial if the circumferential spacing of the here inactive knife from the cutting position 22 is as large as possible. In particular this should be the aim with respect to the upper knife if it projects over the surface 15.
  • FIG. 4 shows the passage of the knives B2 through the cutting gap 16 and which at the lower knife shaft 13 are closer (15°) to the following knives A3 than to the upper knife shaft 12. It is also possible to see there the moving aside of the material web 21 into the recess 23, which can follow on directly to the recess 29.
  • FIG. 5 diagrammatically shows the adjustment of the two knives in order to pass from the engagement position of the knife set A (FIG. 1) to the engagement position of the knife set B (FIG. 6).
  • FIG. 7 shows the knife shafts 12,13 and in particular their mounting support 30 and synchronization means 31, whilst the knife-carrying knife shaft portions 32 are shown in shortened form.
  • bearings 33 On either side of said active knife shaft portions 32 are provided bearings 33, to which are connected the knife shaft synchronizing means 31.
  • the latter is provided on both sides of the knife shafts and contains synchronization gears 34, which engage in one another and synchronize the two shafts in opposition with one another. They are fixed by special clamp collars to the corresponding shaft portion 36. Such clamp collars are described in DE-A-3,608,111.
  • FIG. 8 more particularly shows that to it is fitted a collar 39 with a radial tooth system 40, which is aligned with the radial tooth system 41 of a collar 42 fitted to the hub body 37 radially within the same.
  • a matching radial tooth system 43 on a circular connecting body 44 Facing the radial tooth systems 40,41 is a matching radial tooth system 43 on a circular connecting body 44, which is axially displaceable in the direction of the arrow 45 by means of a hydraulic drive 46.
  • the latter is a circular hydraulic cylinder, which has a circular cylinder portion 47 with a U-shaped cross-section on whose one front side is provided the radial tooth system 43.
  • the piston 48 of the hydraulic cylinder is formed by a ring portion firmly connected to the hub body 37 and which engages in a U-shaped cylinder portion 47.
  • Through the knife shaft hydraulic channels 49 pass into the piston and from there to either side of the pressure medium chamber 50 formed between the piston 48 and the cylinder 47.
  • the cylinder portion 47 with the radial tooth system 43 is axially displaceable in the direction of the arrow 45.
  • the setting means 51 formed by the collars 39,42, the radial tooth systems 40,41,43 and the hydraulic drive 46 are shown in the adjustment position in FIG. 8 in which the radial tooth systems are not in engagement with one another, so that the adjustment of the upper knife shaft with respect to the lower knife shaft shown in FIG. 5 can be carried out.
  • both setting means 51 in FIG. 1 to the right on the upper knife shaft 12 and to the left on the lower knife shaft 13) are disengaged.
  • the rotation of the upper knife shaft e.g.
  • the hydraulic drives 46 are then operated again and press the radial tooth system 43 extending over the two radial tooth systems 40 and 41 into the latter, due to a certain wedge shape of the tooth system performs a precise orientation and once again connects in positive and absolutely backlash-free manner the corresponding knife shafts 12,13 to the associated synchronization gear 34. During operation the hydraulic pressure is maintained. With this type of locking coupling following a relatively rough rotation to be carried out automatically or manually by the operator it is possible to have a repeat-accurate synchronization in the new position in the micro range.
  • the hydraulic drive simplifies operation. It would also be possible to provide a mechanical and optionally manually operable coupling means.
  • FIG. 7 also shows a device for the sector setting of the backlash provided in one of the synchronization gears 34. It could be provided in all four synchronization gears, but at least in one gear per gear pair.
  • the backlash setting means 60 are shown in detail in FIGS. 9 and 10.
  • slots 62 are provided, which extend axially over the entire gear width and are so curved circumferentially that the portion 64 of the gear body between them and the tooth system 63 has a uniform thickness in the present embodiment.
  • the slot 62 can e.g. be made by a laser cut. Axially the slots 62 are closed by a weld 65, so that they form a substantially closed pressure medium pocket 66.
  • the slot extends over a sector with a circumferential angle S, which is dependent on the contour of the eccentricity of the sector S which is to be minimized, the height of the eccentricity which is to be minimized and the thickness of the portion 64.
  • the sector S i.e. the pressure medium pocket extends over approximately 40°.
  • the pressure medium pocket 66 is connected by means of bores 67 to a valve 68, which is located outside the gear area on a hub portion 69 of the gear and is operable from the outside by means of a key face 70.
  • the valve whose valve body is a multiple offset screw bolt with a frustum-shaped valve face 71, which cooperates with a correspondingly shaped valve seat 72, is sealed by a circumferential joint 73.
  • the valve inlet is a sloping bore 74, which somewhat above the valve seat passes laterally into the valve bore, whereas the valve outlet is a central bore 75 communicating with the bores 67.
  • the inlet bore 74 is connected to a pressure medium connection 76, which can be closed by a locking screw 77 (FIG. 10).
  • Each pocket 66 is connected to its own connection 76 via its own valve 68.
  • the sector setting of the backlash is performed in the following way. Following the installation of the gear pair, firstly and in known manner, an adjustment is made to the backlash over the entire circumference. This can e.g. take place by an axial displacement of the gears against one another if they have a slightly conical shape. Such a process is described in DE-A-3,608,111. However, after this adjustment a certain minimum backlash must remain, so that there is no pressure which displaces the lubricant and destroys the tooth profiles, e.g. by Hertz calculated stresses and which could lead to the destruction of the gears. A freedom from backlash should be set only on very small circumferential portions.
  • a pressure medium source is connected to the pressure medium connection 76, e.g. a hydraulic hand pump, which can produce a relatively high pressure of 1000 bar or higher.
  • This pressure is passed via the valve 68 into the pressure medium pocket 66 and "blows" up the latter, in that the portion 64 and therefore the tooth system 63 is slightly outwardly deformed.
  • the drive preferably in the form of a short periodic, speed-variable, direct current motor with a corresponding control (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • General Engineering & Computer Science (AREA)
  • Making Paper Articles (AREA)
  • Nonmetal Cutting Devices (AREA)
US08/442,947 1994-05-19 1995-05-17 Working machine for material webs, particularly paper format cross-cutter Expired - Fee Related US5662018A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4417493.4 1994-05-19
DE4417493A DE4417493A1 (de) 1994-05-19 1994-05-19 Querschneider für Materialbahnen, insbesondere Papier-Formatquerschneider

Publications (1)

Publication Number Publication Date
US5662018A true US5662018A (en) 1997-09-02

Family

ID=6518448

Family Applications (1)

Application Number Title Priority Date Filing Date
US08/442,947 Expired - Fee Related US5662018A (en) 1994-05-19 1995-05-17 Working machine for material webs, particularly paper format cross-cutter

Country Status (4)

Country Link
US (1) US5662018A (de)
EP (1) EP0683020A3 (de)
JP (1) JPH08155887A (de)
DE (1) DE4417493A1 (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6272959B1 (en) * 1998-09-29 2001-08-14 Danieli & C. Officine Meccaniche Spa Continuously rotating shears
US6308605B1 (en) * 1998-10-23 2001-10-30 Bielomatik Leuze Gmbh & Co. Crosscutter for web materials
US20030036468A1 (en) * 2001-07-30 2003-02-20 Kurt Blank Device and method for automatic processing of sheet-shaped print materials with interchangeable functions
US6702280B2 (en) 2001-07-30 2004-03-09 Heidelberger Druckmaschinen Ag Apparatus and process for transporting sheet-shaped print materials
US6776075B1 (en) * 1999-11-10 2004-08-17 Sms Demag Ag High-speed shear for transverse cutting of a thin rolled strip
US7089078B2 (en) 2000-10-26 2006-08-08 Rexroth Indramat Gmbh Method and device for adjusting the degree of engagement of a tool with a web of a materail running past it
US7117776B1 (en) * 1999-11-10 2006-10-10 Sms Demag Ag High-speed shear for transverse cutting of a rolled strip
US7182010B2 (en) 2001-07-30 2007-02-27 Heidelberger Druckmaschinen Ag Apparatus and process for producing different hole patterns in sheet-shaped print materials
US20130036884A1 (en) * 2011-02-10 2013-02-14 Hunkeler Ag Method and apparatus for punching or perforating moving material webs
CN107559408A (zh) * 2017-09-26 2018-01-09 广东万联精工科技有限公司 横切机冷却系统
CN109505951A (zh) * 2018-11-30 2019-03-22 吴永德 一种无间隙齿轮传动机构

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997023398A1 (en) * 1995-12-22 1997-07-03 Wjc Systec A/S Method and device for perforating and/or cutting and/or scoring a web.
US5797305A (en) * 1996-02-12 1998-08-25 Moore Business Forms, Inc. On demand cross web perforation
DE19723513A1 (de) * 1997-06-05 1998-12-10 Jagenberg Papiertech Gmbh Messertrommel für Maschinen zum Querschneiden von Materialbahnen
DE10213978A1 (de) * 2002-03-28 2003-10-09 Roland Man Druckmasch Verfahren zum Querschneiden einer laufenden Bahn
AU2017220657B2 (en) * 2016-02-17 2022-02-03 Tomra Systems Asa Container compressing arrangement and method of operating a container compressing arrangement

Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE602721C (de) * 1934-09-14 Paul Schnuetgen Rotierende Schere fuer mehrere in Bewegung befindliche Walzadern
US2258816A (en) * 1940-02-10 1941-10-14 S & S Corrugated Paper Mach Cyclical knife adjustment
US2345411A (en) * 1941-02-18 1944-03-28 Norfolk Paper Co Inc Method and machine for operating on sheet material
US2918826A (en) * 1954-10-25 1959-12-29 Cooper Bessemer Corp Control device
US3182540A (en) * 1962-12-03 1965-05-11 Ibm Paper forms cutter selectively adjustable to cut equal portions of a predetermined length
FR1524390A (fr) * 1967-04-03 1968-05-10 Siefvert & Fornander Ab Perfectionnements aux cylindres de coupe rotatifs, agencés par paire et munis chacun de son couteau
US3415138A (en) * 1967-05-22 1968-12-10 Ingersoll Milling Machine Co Worm-rack transmission with hydrostatic tooth bearings
US3763959A (en) * 1970-12-23 1973-10-09 Waldrich Werkzeugmasch Hydrostatic lubricating device for the meshing points of cylinder worms and a worm rack
US3844179A (en) * 1973-06-14 1974-10-29 Xerox Corp Gear drive for electrophotographic printing machine
US4072064A (en) * 1977-02-02 1978-02-07 Westinghouse Electric Corporation Anti-backlash gear assembly
SU642097A1 (ru) * 1976-12-03 1979-01-15 Кировский завод по обработке цветных металлов Барабанные летучие ножницы
US4470331A (en) * 1982-06-30 1984-09-11 Precision Strip Technology, Inc. Slitting apparatus
US4493235A (en) * 1983-04-15 1985-01-15 Merrill David Martin Axially adjustable helical cutting blades for rotary web shearing machine
US4881436A (en) * 1986-03-12 1989-11-21 Bielomatik Leuze Gmbh & Co. Transverse cutter for sheet materials
US4912998A (en) * 1986-04-11 1990-04-03 Honda Giken Kogyo Kabushiki Kaisha Gear arrangement
DE4005028A1 (de) * 1989-02-21 1990-08-23 Gaines Pendleton Campbell Jr Querschneider fuer eine mit einer materialbahn beschickte druckerpresse
US5117703A (en) * 1990-07-24 1992-06-02 Man Roland Druckmaschinen Ag Gearwheel for the drive of offset press cylinders
US5152186A (en) * 1990-08-14 1992-10-06 Man Roland Druckmaschinen Gearwheel for the drive of offset press cylinders

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3718776C1 (de) * 1987-06-04 1988-08-25 Strecker Valmet Rotations-Gleichlaufquerschneider
DE3834429C1 (en) * 1988-10-10 1989-12-21 Man Roland Druckmaschinen Ag, 6050 Offenbach, De Gearwheel for driving the cylinders of offset printing machines

Patent Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE602721C (de) * 1934-09-14 Paul Schnuetgen Rotierende Schere fuer mehrere in Bewegung befindliche Walzadern
US2258816A (en) * 1940-02-10 1941-10-14 S & S Corrugated Paper Mach Cyclical knife adjustment
US2345411A (en) * 1941-02-18 1944-03-28 Norfolk Paper Co Inc Method and machine for operating on sheet material
US2918826A (en) * 1954-10-25 1959-12-29 Cooper Bessemer Corp Control device
US3182540A (en) * 1962-12-03 1965-05-11 Ibm Paper forms cutter selectively adjustable to cut equal portions of a predetermined length
FR1524390A (fr) * 1967-04-03 1968-05-10 Siefvert & Fornander Ab Perfectionnements aux cylindres de coupe rotatifs, agencés par paire et munis chacun de son couteau
US3415138A (en) * 1967-05-22 1968-12-10 Ingersoll Milling Machine Co Worm-rack transmission with hydrostatic tooth bearings
US3763959A (en) * 1970-12-23 1973-10-09 Waldrich Werkzeugmasch Hydrostatic lubricating device for the meshing points of cylinder worms and a worm rack
US3844179A (en) * 1973-06-14 1974-10-29 Xerox Corp Gear drive for electrophotographic printing machine
SU642097A1 (ru) * 1976-12-03 1979-01-15 Кировский завод по обработке цветных металлов Барабанные летучие ножницы
US4072064A (en) * 1977-02-02 1978-02-07 Westinghouse Electric Corporation Anti-backlash gear assembly
US4470331A (en) * 1982-06-30 1984-09-11 Precision Strip Technology, Inc. Slitting apparatus
US4493235A (en) * 1983-04-15 1985-01-15 Merrill David Martin Axially adjustable helical cutting blades for rotary web shearing machine
US4881436A (en) * 1986-03-12 1989-11-21 Bielomatik Leuze Gmbh & Co. Transverse cutter for sheet materials
US4912998A (en) * 1986-04-11 1990-04-03 Honda Giken Kogyo Kabushiki Kaisha Gear arrangement
DE4005028A1 (de) * 1989-02-21 1990-08-23 Gaines Pendleton Campbell Jr Querschneider fuer eine mit einer materialbahn beschickte druckerpresse
US5117703A (en) * 1990-07-24 1992-06-02 Man Roland Druckmaschinen Ag Gearwheel for the drive of offset press cylinders
US5152186A (en) * 1990-08-14 1992-10-06 Man Roland Druckmaschinen Gearwheel for the drive of offset press cylinders

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6272959B1 (en) * 1998-09-29 2001-08-14 Danieli & C. Officine Meccaniche Spa Continuously rotating shears
US6308605B1 (en) * 1998-10-23 2001-10-30 Bielomatik Leuze Gmbh & Co. Crosscutter for web materials
US6776075B1 (en) * 1999-11-10 2004-08-17 Sms Demag Ag High-speed shear for transverse cutting of a thin rolled strip
US7117776B1 (en) * 1999-11-10 2006-10-10 Sms Demag Ag High-speed shear for transverse cutting of a rolled strip
US7089078B2 (en) 2000-10-26 2006-08-08 Rexroth Indramat Gmbh Method and device for adjusting the degree of engagement of a tool with a web of a materail running past it
US20030036468A1 (en) * 2001-07-30 2003-02-20 Kurt Blank Device and method for automatic processing of sheet-shaped print materials with interchangeable functions
US6702280B2 (en) 2001-07-30 2004-03-09 Heidelberger Druckmaschinen Ag Apparatus and process for transporting sheet-shaped print materials
US7182010B2 (en) 2001-07-30 2007-02-27 Heidelberger Druckmaschinen Ag Apparatus and process for producing different hole patterns in sheet-shaped print materials
US20130036884A1 (en) * 2011-02-10 2013-02-14 Hunkeler Ag Method and apparatus for punching or perforating moving material webs
CN107559408A (zh) * 2017-09-26 2018-01-09 广东万联精工科技有限公司 横切机冷却系统
CN109505951A (zh) * 2018-11-30 2019-03-22 吴永德 一种无间隙齿轮传动机构

Also Published As

Publication number Publication date
EP0683020A3 (de) 1996-03-20
EP0683020A2 (de) 1995-11-22
JPH08155887A (ja) 1996-06-18
DE4417493A1 (de) 1995-11-23

Similar Documents

Publication Publication Date Title
US5662018A (en) Working machine for material webs, particularly paper format cross-cutter
EP0669208B1 (de) Welle-Montage und Einrichtung für Maschine zum Verarbeiten von Kartonzuschnitten
US5174185A (en) Rotary cutting device for material webs
US4594928A (en) Knife cylinder for working weblike material
US20040003699A1 (en) Rotary apparatus for severing web materials
FI70074C (fi) Skruvrotormaskin
US4205596A (en) Rotary die cutting device
EP1612013B1 (de) Rotationsschneider und Rotationsschneidmaschine mit einem solchen Rotationsschneider
EP1612009B1 (de) Luftverteilungssystem und Rotationsschneidmaschine mit einem Luftverteilungssystem
US5159868A (en) Knife cylinder for processing weblike material
US6279443B1 (en) Die cut roll
US6085626A (en) Rapid adjustment rotary dies
US4791846A (en) Oscillating free wheeling resilient cover for rotary die-cutting anvil
JPS6327237A (ja) 回転ダイカット装置
GB2081144A (en) An arrangement for the radial forming of bodies
FI79964B (fi) Anordning foer skaerning av kontinuerliga band till remsor med formad sidoprofil, speciellt av metallplaot.
US4671154A (en) Knife cylinder for processing a continuous web
US5465641A (en) Cylinder for processing
EP0848996B1 (de) Schneidzylinder für Dokumentenvernichter und Verfahren zur Herstellung desselben
HU183148B (en) Rotary slitting knife
CA2439613C (en) Rotary apparatus and method
CN218362312U (zh) 一种双层组合铣刀
US5226344A (en) Rotary cutting cylinder with floating sheeter blade lock-down bar and method of making same
US5649815A (en) Hydraulic machine and method of producing the contour of a gearwheel of a hydraulic machine
AU773913B2 (en) Rotary machine for a compression or an expansion of a gaseous working fluid and a method for producing a rotor for such a machine

Legal Events

Date Code Title Description
AS Assignment

Owner name: BIELOMATIK LEUZE GMBH & CO., GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:KLEIN, HANSJORG;REEL/FRAME:007514/0994

Effective date: 19950503

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
FP Lapsed due to failure to pay maintenance fee

Effective date: 20010902

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362